Drive force control system

ABSTRACT

A drive force control system to increase a yaw rate greater than the yaw rate achieved by rotating a steering wheel to a maximum angle. A target yaw rate is calculated based on a steering angle of the steering wheel. A first predetermined torque and a second predetermined torque are calculated based on a difference between the target yaw rate and an actual yaw rate. When the steering angle of the steering wheel exceeds a first predetermined angle, a first correction torque to correct the first predetermined torque and a second correction torque to correct the second predetermined torque are calculated n accordance with the steering torque.

CROSS REFERENCE TO RELATED APPLICATION

This application is a continuation of application Ser. No. 15/902,348filed Feb. 22, 2018, which claims the benefit of Japanese PatentApplication No. 2017-030916 filed on Feb. 22, 2017 with the JapanesePatent Office, the disclosures of each of which are incorporated hereinby reference in their entirety.

BACKGROUND Field of the Invention

Embodiments of the present disclosure relate to the art of a drive forcecontrol system for vehicles configured to generate a yaw moment inaccordance with an operation of a steering wheel.

Discussion of the Related Art

JP-A-2005-151623 discloses a behavior control device for electricvehicles that controls torques applied to each drive wheel. According tothe teachings of JP-A-2005-151623, a target turning amount such as a yawrate, and a basic value of target slip angle between a travelingdirection of the vehicle and an orientation of the vehicle arecalculated based on a turning angle of a steering wheel. Then, adifference between drive forces of the right and left drive wheels iscalculated based on the calculated target turning amount and the basicvalue of target slip angle.

Specifically, the control device described in JP-A-2005-151623 isconfigured to calculate the target yaw rate based on the turning angleof the steering wheel, and to control the driving force of the right andleft wheels based on the target yaw rate. According to the teachings ofJP-A-2005-151623, therefore, a yaw moment can be generated in accordancewith a difference of the drive forces between the right and left wheels,in addition to a yaw moment generated in accordance with turning angleof the wheels. For this reason, the turning performance can be improved.However, in the conventional vehicles, a turning angle of the steeringwheel is mechanically limited. That is, if the target yaw rate iscalculated based on a turning angle of the steering wheel, a yaw rategreater than an upper limit angle of the steering wheel cannot beachieved.

SUMMARY

Aspects of embodiments of the present application have been conceivednoting the foregoing technical problems, and it is therefore an objectof embodiments of the present disclosure is to provide a drive forcecontrol system configured to achieve a yaw rate greater than a yaw ratepossible to be achieved by turning a steering wheel to a maximum angle.

The drive force control system according to the embodiment of thepresent application comprises: a drive unit that applies torques to aright wheel and a left wheel; a steering device that turns a pair ofsteered wheels in accordance with an operating amount of a steeringwheel; and a controller that controls the torques applied to the rightwheel and the left wheel. In order to achieve the above-explainedobjective, the controller is configured to: calculate a target yaw ratebased on a steering angle of the steering wheel; calculate a firstpredetermined torque to adjust a required torque of the right wheel anda second predetermined torque to adjust a required torque of the leftwheel, based on a difference between the target yaw rate and an actualyaw rate; obtain a steering torque of the steering wheel; calculate afirst correction torque to correct the first predetermined torque inaccordance with the steering torque and a second correction torque tocorrect the second predetermined torque in accordance with the steeringtorque, when the steering angle of the steering wheel exceeds a firstpredetermined angle; and transmit a signal to the drive unit to achievea first target torque of the right wheel calculated based on the firstpredetermined torque and the first correction torque, and to achieve asecond target torque of the left wheel calculated based on the secondpredetermined torque and the second correction torque.

In a non-limiting embodiment, the controller may be further configuredto calculate the first correction torque and the second correctiontorque based on an increase in the steering torque from a point at whichthe steering angle exceeds the first predetermined angle, when thesteering torque is increased to rotate the steering wheel more than thefirst predetermined angle.

In a non-limiting embodiment, the controller may be further configuredto reduce the first correction torque and the second correction torquein accordance with a length of time to rotate the steering wheel morethan the first predetermined angle.

In a non-limiting embodiment, the controller may be further configuredto offer a warning to a driver when the length of time to rotate thesteering wheel more than the first predetermined angle exceed apredetermined period of time.

In a non-limiting embodiment, the steering device may include a motorthat applies a torque to a transmission mechanism between the steeringwheel and the steered wheels. In addition, the controller may be furtherconfigured to control an output torque of the motor in accordance withthe steering torque of the steering wheel, and to maintain the outputtorque of the motor to the steering torque at a point when the steeringwheel is rotated to the predetermined angle, until the steering angle ofthe steering wheel is reduced to a second predetermined angle that issmaller than the first predetermined angle.

In a non-limiting embodiment, the controller may be further configuredto set an upper limit value of the first correction torque and thesecond correction torque.

Thus, according to the embodiment of the present disclosure, a firstpredetermined torque to adjust the required torque of the right pair ofwheels and the second predetermined torque to adjust the required torqueof the left pair of wheels, are calculated based on the differencebetween the target yaw rate and an actual yaw rate. When the steeringangle of the steering wheel exceeds the first predetermined angle, afirst correction torque to correct the first predetermined torque and asecond correction torque to correct the second predetermined torque arecalculated. The controller transmits a signal to the drive unit toachieve the first target torque of the right pair of wheels calculatedbased on the first predetermined torque and the first correction torque,and to achieve the second target torque of the left pair of wheelscalculated based on the second predetermined torque and the secondcorrection torque. According to the embodiment of the presentdisclosure, therefore, a yaw rate greater than the target yaw rateachieved in accordance with the steering angle of the steering wheel canbe achieved when the steering wheel is turned to the maximum rotationalangle. For this reason, a turning performance of the vehicle can beimproved.

BRIEF DESCRIPTION OF THE DRAWINGS

Features, aspects, and advantages of exemplary embodiments of thepresent disclosure will become better understood with reference to thefollowing description and accompanying drawings, which should not limitthe invention in any way.

FIG. 1 is a cross-sectional view showing one example of a structure ofthe drive unit according to the embodiment of the present disclosure;

FIG. 2 is a schematic illustration showing a structure of a steeringdevice of the vehicle to which the control system according to theembodiment is applied;

FIG. 3 is a schematic illustration showing one example of a structure ofthe vehicle to which the control system according to the embodiment isapplied;

FIG. 4 is a block diagram showing functions of a first ECU;

FIG. 5 is a flowchart showing a routine according to the first controlexample;

FIG. 6 is a flowchart showing steps S1 to S15 in a routine according tothe second control example;

FIG. 7 is a flowchart showing steps S16 to S31 in the routine accordingto the second control example;

FIG. 8 is a flowchart showing steps S32 to S38 in the routine accordingto the second control example; and

FIG. 9 is a time chart showing temporal changes in of a steering torque,an output torque of an EPS motor, an correction torque, and an upperlimit value of the correction torque during execution of the routineaccording to the second control example.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT(S)

Embodiment of the present disclosure will now be explained withreference to the accompanying drawings. Turning now to FIG. 1, there isshown one example of a structure of a drive unit to which the driveforce control system according to the present disclosure is applied. Ascan be seen from FIG. 1, a structure of the drive unit 1 issubstantially symmetrical across a width center of the vehicle. In thefollowing explanation, only a configuration on the right half in thefigure will be explained, and an explanation for the left half will beomitted except for a configuration different from that of the righthalf. In FIG. 1, accordingly, the reference letter “R” designatesmembers arranged in the right half of the drive unit 1, and thereference letters “L” designates members arranged in the left half ofthe drive unit 1. In the flowing explanation, the members in the righthalf of the drive unit 1 will be called the “first member”, and themembers in the left half of the drive unit 1 will be called the “secondmember” as necessary.

The drive unit 1 includes a motor 2 serving as a prime mover of avehicle. For example, a motor-generator such as a permanent magnetsynchronous motor may be used as the drive motor, as in the case ofconventionally known motors serving as prime movers of hybrid vehiclesand electric vehicles.

An output gear 4 is fitted onto a laterally inner end of an output shaft3 of the motor 2 extending widthwise, and a countershaft 5 extendsparallel to the output shaft 3. A counter driven gear 6 that isdiametrically larger than the output gear 4 is fitted onto a laterallyouter portion of the countershaft 5, and a pinion gear 7 that isdiametrically smaller than the counter driven gear 6 is also fitted ontoa laterally inner portion of the countershaft 5 to be meshed with afinal reduction gear 8 that is diametrically larger than the pinion gear7.

A cylindrical shaft 9 is inserted into the final reduction gear 8 aboutthe rotational center thereof in such a manner as to protrude laterallyoutwardly while opening to laterally outside. A laterally inner end of adriveshaft 10 is splined into the opening of the cylindrical shaft 9,and a drive wheel 11 is attached to a laterally outer end of thedriveshaft 10.

A disc-shaped brake rotor 12 made of magnetic material is fitted onto alaterally outer end of the output shaft 3. An annular brake stator 13faces the brake rotor 12. The brake stator 13 is splined into a casing Cso that the brake stator 13 is allowed to move toward the brake rotor 12but not allowed to rotate. The brake stator 13 is provided with a coil14 so that the brake stator 13 is brought into contact to the brakerotor 12 by an electromagnetic force established by energizing the coil14.

A brake torque is applied to the brake rotor 12 by frictionallycontacting the brake stator 13 to the brake rotor 12. Thus, the brakestator 13, the brake rotor 12, and the coil 14 form a friction brake 15.

An extension shaft 16 is attached to the leading end of the first outputshaft 3R closer to the width center of the vehicle than the first outputgear 4R. An annular clutch disc 17 is fitted onto the extension shaft 16to be rotated integrally therewith.

A bottomed-cylindrical cover shaft 18 holding the clutch disc 17 in ahollow space is attached to the leading end of the second output shaft3L closer to the width center of the vehicle than the second output gear4L.

An annular pressure plate 19 is interposed between a bottom face of thecover shaft 18 and the clutch disc 17. The pressure plate 19 is made ofmagnetic material, and is splined into the cover shaft 18 to be rotatedintegrally with the cover shaft 18 while being allowed to move in theaxial direction of the cover shaft 18.

A spring 20 is interposed between the bottom face of the cover shaft 18and the pressure plate 19 to push the pressure plate 19 toward theclutch disc 17.

A coil 21 is provided on the outer side of the cover shaft 18. The coil21 generates an electromagnetic force upon being energized, so that thepressure plate 19 is isolated away from the clutch disc 17 against aspring force of the spring 20.

The clutch disc 17, the pressure plate 19, the spring 20, and the coil21 form an electromagnetic clutch (to be simply referred to as a clutchhereinafter) 22. When the coil 21 is not energized, the clutch disc 17and the pressure plate 19 are contacted to each other by the springforce of the spring 20 to be rotated integrally. When the coil 21 isenergized, a torque transmitting capacity between the clutch disc 17 andthe pressure plate 19 is set in accordance with the electric powerapplied to the coil 21.

Thus, the first motor 2R and the second motor 2L can be rotatedintegrally while transmitting a torque therebetween by frictionallyengaging the pressure plate 19 and the clutch disc 17 without energizingthe coil 21. A torque transmitting capacity between the pressure plate19 and the clutch disc 17 can be reduced by energizing the coil 21. As aresult, the first motor 2R and the second motor 2L rotate relatively toeach other, whereby a torque transmitted between the first motor 2R andthe second motor 2L can be reduced.

The brake torque applied to the drive wheels 11R and 11L cannot bemaintained when the power is off to park the vehicle. In order tomaintain a frictional contact between the first brake rotor 12R and thefirst brake stator 13R thereby halting the drive wheels 11R and 11L evenwhen the power is off, the drive unit 1 is provided with a parking lockdevice 23. Specifically, the parking lock device 23 comprises an annularmovable plate 24 opposed to the first brake rotor 12R across the firstbrake stator 13R, a feed screw mechanism 25, and a brake motor 26 thatactuates the feed screw mechanism 25.

The feed screw mechanism 25 is adapted to translate a rotary motion ofthe brake motor 26 into a linear motion thereby pushing the movableplate 24 toward the first brake stator 13R so as to bring the firstbrake stator 13R into frictional contact to the first brake rotor 12R.That is, the feed screw mechanism 25 keeps the first output shaft 3Rstopping even if current supply to the brake motor 26 is interrupted.Thus, the feed screw mechanism 25 generates forward thrust force bygenerating forward torque by the brake motor 26, and the forward thrustforce is applied to the first brake stator 13R. Consequently, the firstbrake stator 13R is frictionally engaged with the first brake rotor 12Rto halt the first output shaft 3R. By contrast, the first output shaft3R is allowed to rotate by generating a reverse torque by the brakemotor 26 to withdraw the first brake stator 13R from the first brakerotor 12R. That is, the brake force for stopping the rotation of thefirst output shaft 3R is canceled.

Specifically, reversed efficiency of the feed screw mechanism 25 totranslate the linear motion into the rotational motion is adjusted to belower than forward efficiency to translate the rotational motion intothe linear motion. According to an embodiment, therefore, the firstoutput shaft 3R may be halted by pushing the movable plate 24 and thefirst brake stator 13R toward the first brake rotor 12R by the feedscrew mechanism 25. Therefore, the first output shaft 3R may be haltedby the parking lock device 23 even if the current supply to the firstcoil 14R and the brake motor 26 is stopped while the feed screwmechanism 25 is operated by the brake motor 26 to halt the first outputshaft 3R.

Thus, when the vehicle is parked, the current supply to the coil 21 isstopped and hence the clutch 22 is brought into engagement. In thissituation, therefore, rotation of the second output shaft 3L is alsostopped by stopping the rotation of the first output shaft 3R by theparking lock device 23. In other words, the brake torques applied to thedrive wheels 11R and 11L can be maintained. The parking lock device 23may be arranged in such a manner as to stop the rotation of the secondoutput shaft 3L, or may be arranged in such a manner as to stop therotation of the first countershaft SR instead of the first output shaft3R, for example.

As described, in the drive unit 1, the right and the left drive wheels11R and 11L may be rotated integrally to propel the vehicle by engagingthe clutch 22 completely to apply the same torques to the right and theleft drive wheels 11R and 11L. For example, the vehicle can be propelledby a torque generated by at least one of the first motor 2R and thesecond motor 2L. In this case, the torque generated by one of the firstmotor 2R and the second motor 2L may be regenerated partially by theother one of the motors. Further, one of the first motor 2R and thesecond motor 2L can generate a large torque, and the other one of themotors can generate a torque in an amount corresponding to the shortage.Thus, output torques of the motors 2R and 2L can be adjusted asappropriate.

When the right and the left drive wheels 11R and 11L are rotatedrelative to each other during turning or the other like occasions, orwhen differentiating torques transmitted to the right and the left drivewheels 11R and 11L, the vehicle can be propelled by generating a torqueby at least one of the motors 2R and 2L while causing a slip in theclutch 22. Further, the vehicle can be propelled by generating the drivetorque by one of the motors 2R and 2L while regenerating part of thedrive torque by the other one of the motors 2R and 2L. For this purpose,the output torques of the motors 2R and 2L can be adjusted asappropriate.

When a speed difference or a torque difference between the right and theleft drive wheels 11R and 11L is equal to or larger than a predeterminedvalue, the outputs of the right and the left drive wheels 11R and 11Lmay be appropriately adjusted by completely disengaging the clutch 22.In this situation, the motor 2R (2L) connected to the outer wheel may beoperated as a motor and the motor 2R (2L) connected to the inner wheelmay be operated as a generator. Instead, only the motor 2R (2L)connected to the outer wheel may be operated to generate a torque.

The front wheels 11R and 11L are turned by a steering device 27 shown inFIG. 2 in accordance with the operation amount (turning angle) of thesteering wheel 28.

In the steering device 27, a rotation of the steering shaft 29 connectedto the steering wheel 28 is transmitted the to a rack bar 31 of atransmission mechanism such as a rack and pinion mechanism 30. A rightdrive wheel 11R is connected to a right end of the rack bar 31 through aright tie rod 42R and a knuckle (not shown), and a left drive wheel 11Lis connected to a left end of the rack bar 31 through a left tie rod 42Land a knuckle (not shown).

An electric power steering motor (to be abbreviated as the “EPS motor”hereinafter) 44 is connected to the steering shaft 29 via a speedreducer 43, and torque of the steering shaft 29 is increased by anoutput torque of the EPS motor 44.

A steering torque sensor 45 that detects a torque of the steering shaft29, and a steering angle sensor 46 that detects a turning angle of thesteering shaft 29 are arranged on the steering shaft 29 between thesteering wheel 28 and the speed reducer 43.

In the steering device 27, orientations of the right front wheel 11R andthe left front wheel 11L are turned by rotational motion (i.e., torque)of the steering wheel 28 transmitted through the rack and pinionmechanism 30. In order to reduce an effort of the driver to turn thefront wheels 11R and 11L by rotating the steering wheel 28, the EPSmotor 44 generates an assist torque to rotate the steering wheel 28 inaccordance with a torque detected by the steering torque sensor 45. Inorder to restrict a turning angle of the steering wheel 28 within apredetermined range, a movable range of the rack bar 31 is restricted bya restricting mechanism (not shown).

Next, an example of a configuration of a control system S for a vehicleVe including the drive unit 1 described above will be described. FIG. 2is a diagram schematically showing an example of the configuration ofthe system. As illustrated in FIG. 2, the vehicle Ve is a four wheeldrive (4WD) layout vehicle in which a first drive unit 1 is arranged inthe front side of the vehicle Ve and a second drive unit 1′ is arrangedin the rear side of the vehicle Ve substantially symmetrical across thelongitudinal center of the vehicle Ve. In the flowing explanation, themembers of the second drive unit 1′ with the same configuration as themembers (including the first motor 2R) provided in a torque transmissionpath between the first motor 2R and the right drive wheel 11R in thefirst drive unit 1 will be called the “third member”. The members of thefirst drive unit 1 with the same configuration as the members (includingthe second motor 2L) provided in a torque transmission path between thesecond motor 2L and the left drive wheel 11L in the first drive unit 1will be called the “fourth member”. The clutch and the parking lockdevice in the second drive unit 1′, as well as the members of these,will be called a “second clutch”, a “second parking lock device”, andthe “second member”. The apostrophe on the reference numeral designatesmembers of the second drive unit 1′, for the distinction from themembers of the first drive unit 1.

In the first drive unit 1, the first motor 2R, the second motor 2L, andthe coils 14R, 14L, and 21 receive electric power from a high-voltagepower storage device 47 including a battery and a capacitor, as aconventional power storage device used in hybrid vehicles and electricvehicles. Likewise, in the second drive unit 1, the first motor 2R′, thesecond motor 2L′, and the coils 14W, 14L′, and 21′ also receive theelectric power from the power storage device 47. The power storagedevice 47 is charged with the power generated by the motors 2R, 2L, 2R′,and 2L′. In the following explanation, the motor 2R′ of the second driveunit 2′ will be called the “the third motor” 2R′, and the motor 2L′ ofthe second drive unit 2′ will be called the “the fourth motor” 2L′.

A first inverter 48 is interposed between the power storage device 47and the motors 2R and 2L, and the first inverter 48 is adapted to switchbetween direct current and alternate current, and to control values andfrequencies of current supplied to the motors 2R and 2L. The seconddrive unit 1′ is also provided with a second inverter 49 that cancontrol a value and a frequency of the current supplied to the motors2R′ and 2L′.

A first electronic control unit 50 (to be abbreviated as the “first ECU”hereinafter) is provided to control the motors 2R and 2L and the coils14R, 14L, and 21 of the first drive unit 1, as well as the motors 2R′and 2L′ and the coils 14R′, 14L′, and 21′ of the second drive unit 1′.The first ECU 50 as a “controller” of the embodiment mainly includes amicrocomputer as in any known ECUs installed in vehicles. FIG. 4 is ablock diagram illustrating functions of the first ECU 50.

Signals representing posture of the vehicle Ve and operating conditionsare sent to the first ECU 50, and the first ECU 50 transmits controlsignal to the first inverter 48 and the second inverter 49 based on theincident signals, preinstalled formulas and maps, and the like.Specifically, the first ECU 50 transmits control signals for controllingoutput torques of the motors 2R, 2L, 2R′ and 2L, control signals forcontrolling torque transmitting capacities of the clutches 22 and 22,control signals for controlling the friction brakes 15 and 15′ and soon. The control signals sent from the first ECU 50 to the first inverter48 and the second inverter 99 are obtained while taking account ofconventionally known Antilock Brake system (ABS), Traction Control(TRC), Electronic Stability Control (ESC), Dynamic Yaw rate Control(DYC), and the like.

For example, the first ECU 50 receives signals from an acceleratorsensor 51 that detects a depression of an accelerator pedal, a firstbrake pedal sensor 52 that detects a pedal force applied to the brakepedal, a second brake pedal sensor 53 that detects a depression of thebrake pedal, a steering angle sensor 46 that detects a steering angle ofthe steering wheel 28, and the steering torque sensor 45 that detects asteering torque of the steering wheel 28. For example, the first ECU 50also receives signals representing data about the posture of the vehicleVe, from a first G sensor 54 that detects longitudinal acceleration ofthe vehicle Ve, a second G sensor 55 that detects lateral accelerationof the vehicle Ve, a yaw rate sensor 56 that detects a yaw rate of thevehicle Ve, and wheel speed sensors 58, 59, 60, and 61 that respectivelydetect rim speeds of the right front wheel 11R, the left front wheel11L, the right rear wheel 57R, and the left rear wheel 57L.

A first auxiliary battery 62 is provided to supply power for operatingthe first ECU 50 and for controlling a transistor (not illustrated)installed in the first inverter 48. The first auxiliary battery 62 isset to be at a lower voltage than the power storage device 27.

To this end, in the example illustrated in FIG. 3, a second ECU 63 isprovided independently from the first ECU 50. In order to control abrake force in the event of failure of the first ECU 50, the second ECU63 is electrically connected to the parking lock devices 23 and 23′(specifically, the brake motors 26 and 26′), and a second auxiliarybattery 64 is connected to the second ECU 45.

Next, a control example for determining the output of each of the motors2R, 2L, 2R′, and 2L′ will be described with reference to FIG. 5. Routinillustrated in FIG. 5 is executed by the first ECU 50. At step S1,required torque T_(dr) of the vehicle Ve is calculated based on aposition of the accelerator pedal, a depression of the brake pedal or apedal force applied to the brake pedal, wheel speeds, a longitudinalacceleration, and so on. Details of calculation at step S1 is describedin Japanese Patent Application No. 2015-253254.

Then, in order to improve a turning stability by executing theElectronic Stability Control (ESC) and Dynamic Yaw rate Control (DYC), afirst target torque T^(r) _(t) of the right pair drive of wheels Dr as atotal value of a torque of the right front wheel 11R and a torque of theright rear wheel 57R is calculated, and a second target torque T^(l)_(t) of the left pair of wheels Dl as a total value of a torque of theleft front wheel 11L and a torque of the left rear wheel 57L iscalculated.

To this end, a first required torque T^(r) _(r) of the right pair ofwheels Dr, a second required torque T^(l) _(r) of the left pair ofwheels Dl, and a first distribution torque T^(r) _(di) to the right pairof wheels Dr and a second distribution torque T^(l) _(di) to the leftpair of wheels Dl to achieve a required yaw rate, so as to outputtorques equally from the first pair of wheels Dr and from the secondpair of wheels Dl to achieve a required drive force are calculated.Then, a first target torque T^(r) _(t) of the outer pair of wheels(e.g., the right pair of wheels Dr) is calculated by adding the firstdistribution torque T^(r) _(di) to the first required torque T^(r) _(r)of the right pair of wheels Dr, and a second target torque T^(l) _(t) ofthe inner pair of wheels (e.g., the left pair of wheels Dl) iscalculated by subtracting the second distribution torque T^(l) _(di)from the second required torque T^(l) _(r) of the left pair of wheelsDl.

In order to obtain the distribution torques T^(r) _(di) and T^(l) _(di),at step S2, a target yaw rate γ_(tgt) is calculated based on a steeringangle δ of the steering wheel 28, using the following formula:

γ_(tgt)=((1/(1+A·V _(b) ²))·(V _(b) /l))·(δ/n),

where “A” is a target stability factor, “l” represents a wheelbase, and“n” is a steering gear ratio calculated based on a ratio between thesteering angle δ of the steering shaft 29 and a turning angle of thepair of front wheels 11R and 11L.

Then at step S3, a difference Δγ between the target yaw rate γ_(tgt) andan actual yaw rate γ_(real) is calculated. Thereafter, at step S4, afirst predetermined torque T^(r) _(b) subtracted from the first requiredtorque T^(l) _(r) of the one of the right and left pairs of wheels(e.g., the right pair of wheels Dr), and a second predetermined torqueT^(l) _(b) added to the second required torque T^(l) _(r) of the otherpair of wheels (e.g., the left pair of wheels Dl), are calculated basedon the difference Δγ. That is, torques of one of the right and leftpairs of the wheels are increased and torques of the other pairs of thewheels are reduced in such a manner as to achieve the target yaw ratewithout changing the drive force to propel the vehicle Ve. Specifically,absolute values of the first predetermined torque T^(r) _(b) and thesecond predetermined torque T^(l) _(b) are equal to each other, and thefirst predetermined torque T^(r) _(b) and the second predeterminedtorque T^(l) _(b) are calculated using the following formulas:

T ^(r) _(b) =−K _(γ)·Δγ; and

T ^(l) _(b) =K _(γ)·Δγ.

Thereafter, it is determined at step S5 whether or not an absolute valueof the steering angle δ of the steering wheel 28 is equal to or greaterthan a first predetermined angle α. Such determination at step S5 isexecuted to determine whether or not the steering wheel 28 is turned tothe maximum angle. To this end, the first predetermined angle α is setto the maximum rotational angle of the steering wheel 28. Specifically,a right (i.e., clockwise) rotational angle of the steering wheel 28 is apositive value, and a left (i.e., counterclockwise) right rotationalangle of the steering wheel 28 is a negative value. At step S5,therefore, an absolute value of the steering angle δ of the steeringwheel 28 is compared to the first predetermined angle α.

When the driver requires a yaw rate greater than that achieved byturning the steering wheel 28 to the maximum rotational angle, thedriver would attempt to further rotate the steering wheel 28 so that asteering torque T_(δ) of the steering wheel 28 is increased. In order tofulfill such requirement of the driver, if the steering angle δ of thesteering wheel 28 is equal to or greater than the first predeterminedangle α so that the answer of step S5 is YES, the routine progresses tostep S6 to calculate the first distribution torque T^(r) _(di) to theright pair of wheels Dr and the second distribution torque T^(l) _(di)to the left pair of wheels Dl. Specifically, the first distributiontorque T^(r) _(di) is calculated by correcting the first predeterminedtorque T^(r) _(b) in accordance with the steering torque T_(δ), and thesecond distribution torque T^(l) _(di) is calculated by correcting thesecond predetermined torque T^(r) _(b) in accordance with the steeringtorque T_(δ). Thus, the predetermined torques T^(r) _(b) and T^(l) _(b)calculated based on the target yaw rate γ_(tgt) are corrected inaccordance with the steering torque T_(δ).

At step S6, more specifically, the first distribution torque T^(r) _(dl)is calculated by adding a first correction torque T^(r) _(add) to thefirst predetermined torque T^(r) _(b), and the second distributiontorque T^(l) _(di) is calculated by adding a second correction torqueT^(l) _(add) to the second predetermined torque T^(l) _(b). Magnitudesof the correction torques T^(r) _(add) and T^(l) _(add) are identical toeach other, but directions of the correction torques T^(r) _(add) andT^(l) _(add) are opposite to each other. That is, one of thepredetermined torques T^(r)b and T^(l) _(b) (e.g., the firstpredetermined torque T^(r) _(b)) calculated at step S4 is set to anegative value. At step S6, therefore, the second predetermined torqueT^(r) _(b) as a positive value is increased, and the first predeterminedtorque T^(r) _(b) as a negative is reduced. For example, values of thecorrection torques T^(r) _(add) and T^(l) _(add) may be determined withreference to a map determining the correction torques T^(r) _(add) andT^(l) _(add) in such a manner that the correction torques T^(r) _(add)and T^(l) _(add) are increased with an increase in the steering torqueT_(δ). Such map is prepared based on a result of an experiment orsimulation and installed in the first ECU 50.

By contrast, if the steering angle δ of the steering wheel 28 is smallerthan the first predetermined angle α so that the answer of step S5 isNO, the routine progresses to step S7 to employ the first predeterminedtorque T^(r) _(b) calculated at step S4 as the first distribution torqueT^(r) _(di) without correcting, and to employ the second predeterminedtorque T^(l) _(b) calculated at step S4 as the second distributiontorque T^(l) _(di) without correcting.

After thus setting the distribution torques T^(r) _(di) and T^(l) _(di)at step S6 or S7, the routine progresses to step S8 to calculate thefirst target torque T^(r) _(t) by adding the first distribution torqueT^(r) _(di) to the first required torque T^(r) _(r), and to calculatethe second target torque T^(l) _(t) by adding the second distributiontorque T^(l) _(di) to the second required torque T^(l) _(r). Thereafter,the routine returns. Consequently, command signals for controllingoutput torques of the motors 2R, 2L, 2R′, and 2L, and command signalsfor controlling torque transmitting capacities of the clutches 22 and22′ are set and transmitted in accordance with the first target torqueT^(r) _(t) and the second target torque T^(l) _(t) calculated at stepS8. Optionally, the first target torque T^(r) _(t) and the second targettorque T^(l) _(t) may be further corrected taking account of a verticalforce at each wheel, and a friction coefficient (or slip rate) between aroad surface and each wheel.

By thus executing the routine shown in FIG. 5, a yaw rate greater thanthe target yaw rate γ_(tgt) achieved in accordance with the steeringangle δ of the steering wheel 28 can be achieved when the steering wheel28 is turned to the maximum rotational angle. According to theembodiment, therefore, a turning performance of the vehicle can beimproved.

As described, the EPS motor 44 is adapted to generate torque inaccordance with the steering angle δ of the steering wheel 28. If thesteering wheel 28 is turned to the maximum angle for a long period oftime, a temperature of the EPS motor 44 may be raised and consequentlythe EPS motor 44 may be thermally damaged. As also described, the motorsof the outer pairs of wheels increase the torques of the outer pairs ofwheels during turning, and if output torques of those motors areincreased for a long period of time, temperatures of those motors mayalso be increased.

A routine executed to limit damages on the EPS motor 44 and the motors2R, 2L, 2R′, and 2L′ is shown in FIGS. 6 to 8. The routines inflowcharts shown in FIGS. 6 to 8 may be implemented consecutively, butare separately shown in FIGS. 6 to 8 for the sake of explanation. In theroutine shown in FIG. 6, the foregoing steps S1 to S5 are also executed.

In the routine shown in FIG. 6, if the steering angle δ of the steeringwheel 28 is equal to or greater than the first predetermined angle α sothat the answer of step S5 is YES, it is determined whether the steeringangle δ exceeds the first predetermined angle α first time since thesteering wheel 28 is started to be turned. In this case, the routineprogresses to step S10 to determine whether or not a determination flagF_(lk) is turned off. Specifically, the determination flag F_(lk) isturned on when the steering angle δ exceeds the first predeterminedangle α, and turned off when the steering angle δ falls below theafter-mentioned second predetermined angle β.

If the determination flag F_(lk) is turned off so that the answer ofstep S10 is YES, the routine progresses to step S11 to turn on thedetermination flag F_(lk). Then, at step S12, a steering torque T_(δmem)of a steering torque T_(δ) at a point when the steering angle δ exceedsthe first predetermined angle α is stored in the first ECU 50.

As described, according to the embodiment, the distribution torquesT^(r) _(di) and T^(l) _(di) are increased greater than the torquescalculated based on the target yaw rate γ_(tgt). However, in order tolimit the thermal damages on the motors 2R, 2L, 2R′, and 2L′, and toreduce uncomfortable feeling when reducing the distribution torquesT^(r) _(di) and T^(l) _(di) upon satisfaction of the after-mentionedcondition, it is preferable to restrict torques to increase thedistribution torques T^(r) _(di) and T^(l) _(di). To this end, theroutine progresses to step S13 to set an upper limit value T_(u) of thefirst correction torque T^(r) _(add) added to the first predeterminedtorque T^(r) _(b), and the second correction torque T^(l) _(add) addedto the second predetermined torque T^(l) _(b). The upper limit valueT_(u) is set taking account of the above-explained reasons, and storedin the first ECU 50.

As described, the EPS motor 44 generates a torque in accordance with thesteering torque T_(δ). That is, if the torque is further applied to thesteering wheel 28 after turning the steering wheel 28 to the maximumangle, the output torque of the EPS motor 44 may be further increased.In this situation, it is difficult to determine whether the steeringtorque T_(δ) detected by the torque sensor 45 is increased to increasethe yaw rate in line with the driver's intension, or increased with anincrease in the output torque of the EPS motor 44. In other words, it isdifficult to properly determine an increase in the steering torque T_(δ)in line with the driver's intension. For this reason, the routineprogresses to at step S14 to turn on a maintenance flag F_(tqkp) tomaintain the output torque of the EPS motor 44 to a constant torque.

Then, the routine progresses to step S15 to start a measurement ofelapsed time from a point at which the output torque of the EPS motor 44is maintained to the constant torque. In other words, an elapsed time ismeasured from a point at which the maintenance flag F_(tqkp) is turnedon. If the determination flag F_(lk) is has already been turned on sothat the answer of step S10 is NO, the routine skips steps S11 to S15.

After starting the measurement of elapsed time at step S15, or if theanswer of step S10 is NO, the routine progresses to step S16 todetermine whether it is necessary to increase a difference betweentorques of the right pair of wheels Dr and the left pair of wheels Dl toachieve the required yaw rate. At step S16, specifically, it isdetermined whether or not the following condition is satisfied:

δ>0 and T_(δ)>T_(δmem); or

δ<0 and T_(δ)<T_(δmem).

Specifically, the steering angle δ is increased positively by applyingthe positive steering torque T_(δ) to the steering wheel 28, thesteering angle δ is increased negatively by applying the negativesteering torque T_(δ) to the steering wheel 28. As described, thesteering torque T_(δmem) has been stored in the first ECU 50 at stepS12. That is, at step S16, it is determined whether or not the torque isapplied to the steering wheel 28 to rotate the steering wheel 28 furtherthan the maximum angle.

If it is not necessary to increase the difference between the torques ofthe right pair of wheels Dr and the left pair of wheels Dl so that theanswer of step S16 is NO, the routine progresses to step S17 to set eachof the first correction torque T^(r) _(add) and the second correctiontorque T^(l) _(add) individually to zero. By contrast, if it isnecessary to increase the difference between the torques of the rightpair of wheels Dr and the left pair of wheels Dl so that the answer ofstep S16 is YES, the routine progresses to step S18 to calculate each ofthe first correction torque T^(r) _(add) and the second correctiontorque T^(l) _(add) individually based on the steering torque T_(δ), asexpressed by the following expressions:

T ^(r) _(add)=−(K _(t)·(T _(δ) −T _(δmem))); and

T ^(l) _(add) =K _(t)·(T _(δ) −T _(δmem)).

At step S18, specifically, the first correction torque T^(r) _(add) andsecond correction torque T^(l) _(add) are calculated individually bymultiplying a change in the steering torque (T_(δ)−T_(δmem)) by acoefficient Kt, when the steering torque T_(δ) is applied to thesteering wheel 28 to increase the steering angle δ greater than themaximum angle. To this end, the coefficient Kt may be based on a resultof an experiment or simulation and installed in the first ECU 50.

After thus setting the first correction torque T^(r) _(add) and thesecond correction torque T^(l) _(add) at step S17 or S18, the firstcorrection torque T^(r) _(add) and the second correction torque T^(l)_(add) are corrected in accordance with a length of time to maintain theoutput torque of the EPS motor 44 to the constant torque. Specifically,at step S19, it is determined whether or not a length of time Timer_(OH)to maintain the output torque of the EPS motor 44 to the constant torqueis longer than a predetermined period of time TM_(OH) that is set insuch a manner that the EPS motor 44 will not be damaged excessively bymaintaining the output torque of the EPS motor 44 to the constanttorque.

If the length of time Timer_(OH) is longer than the predetermined periodof time TM_(OH) so that the answer of step S19 is YES, the routineprogresses to step S20 to offer a warning to the driver by turning on aflag to actuate a warning device (not shown). If the output torque ofthe EPS motor 44 is maintained to the constant torque longer than thepredetermined period of time TM_(OH), a failure may be caused in the EPSmotor 44. In addition, as explained later, the yaw rate will be reducedby reducing the correction torques T^(r) _(add) and T^(l) _(add). Forthese reasons, the warning is emitted at step S20 to urge the driver toreduce the steering angle δ of the steering wheel 28. Consequently, theoutput torque of the EPS motor 44 will be reduced.

Then, at step S21, a predetermined value T_(sub) is subtracted from theupper limit value T_(u) of the correction torques T^(r) _(add) and T^(l)_(add). Specifically, the predetermined value T_(sub) is set in such amanner as to prevent an excessive reduction in the yaw rate and to limitdamage on the EPS motor 44. That is, the upper limit value T_(u) of thecorrection torques T^(r) _(add) and T^(l) _(add) is reduced gradually byrepeating the routine shown in FIGS. 6 to 8.

Then, it is determined at step S22 whether or not the upper limit valueT_(u) of the correction torques T^(r) _(add) and T^(l) _(add) is greaterthan zero. In other words, it is determined whether the correctiontorques T^(r) _(add) and T^(l) _(add) can be outputted. If the upperlimit value T_(u) is greater than zero so that the answer of step S22 isYES, the routine progresses to step S23 to determine whether or not anabsolute value of the first correction torque T^(r) _(add) for the rightpair of wheels Dr is greater than the upper limit value T_(u). If theabsolute value of the first correction torque T^(r) _(add) for the rightpair of wheels Dr is greater than the upper limit value T_(u) so thatthe answer of step S23 is YES, the routine progresses to step S24 to setthe first correction torque T^(r) _(add) to the current upper limitvalue T_(u). As described, the predetermined value T_(sub) is subtractedfrom the upper limit value T_(u) every time the routine is repeated,therefore, the first correction torque T^(r) _(add) is reduced agradually by repeating steps S23 and S24. Consequently, thermal damageson the first motor 2R and the third motor 2R′ can be reduced duringrotating the right pair of wheels Dr by the torques of the first motor2R and the third motor 2R′ while disengaging the clutches 22 and 22′.

Likewise, at step S25, it is determined whether or not an absolute valueof the second correction torque T^(l) _(add) for the left pair of wheelsDl is greater than the upper limit value T_(u). If the absolute value ofthe second correction torque T^(l) _(add) for the left pair of wheels Dlis greater than the upper limit value T_(u) so that the answer of stepS25 is YES, the routine progresses to step S26 to set the secondcorrection torque T^(l) _(add) to the current upper limit value T_(u).As described, the predetermined value T_(sub) is subtracted from theupper limit value T_(u) every time the routine is repeated, therefore,the second correction torque T^(l) _(add) is reduced gradually byrepeating steps S25 and S26. Consequently, thermal damages on the secondmotor 2L and the fourth motor 2L′ can be reduced during rotating theleft pair of wheels Dr by the torques of the second motor 2L and thefourth motor 2L′ while disengaging the clutches 22 and 22′. Otherwise,if the absolute value of the first correction torque T^(r) _(add) forthe right pair of wheels Dr is smaller than the upper limit value T_(u)so that the answer of step S23 is NO, and if the absolute value of thesecond correction torque T^(l) _(add) for the left pair of wheels Dl issmaller than the upper limit value T_(u) so that the answer of step S25is NO, it is unnecessary to reduce the correction torques T^(r) _(add)and T^(l) _(add). in those cases, therefore, the routine skips steps S24and S26.

By contrast, if the upper limit value T_(u) is smaller than zero so thatthe answer of step S22 is NO, the routine progresses to step S27 to seteach of the first correction torque T^(r) _(add) and the secondcorrection torque T^(l) _(add) individually to zero. Then, themaintenance flag F_(tqkp) is turned off at step S28, and the upper limitvalue T_(u) is set to zero at step S29.

Then, at step S30, the first distribution torque T^(r) _(di) iscalculated by adding the first correction torque T^(r) _(add) to thefirst predetermined torque T^(r) _(b) calculated at step S4, and thesecond distribution torque T^(l) _(di) is calculated by adding a secondcorrection torque T^(l) _(add) to the second predetermined torque T^(l)_(b) calculated at step S4. Thereafter, at step S31, the first targettorque T^(r) _(t) is calculated by adding the first distribution torqueT^(r) _(di) to the first required torque T^(r) _(r), and the secondtarget torque T^(l) _(t) is calculated by adding the second distributiontorque T^(l) _(di) to the second required torque T^(l) _(r). Thereafter,the routine returns. Consequently, command signals for controllingoutput torques of the motors 2R, 2L, 2R′, and 2L′, and command signalsfor controlling torque transmitting capacities of the clutches 22 and22′ are set and transmitted in accordance with the first target torqueT^(r) _(t) and the second target torque T^(l) _(t) calculated at stepS31. Optionally, the first target torque T^(r) _(t) and the secondtarget torque T^(l) _(t) may be further corrected taking account of avertical force at each wheel, and a friction coefficient (or slip rate)between a road surface and each wheel.

Otherwise, if the absolute value of the steering angle δ of the steeringwheel 28 is smaller than the first predetermined angle α so that theanswer of step S5 is NO, the routine progresses to step S32 to determinewhether or not the absolute value of the steering angle δ is greaterthan the second predetermined angle β. Specifically, the secondpredetermined angle β is smaller than the first predetermined angle α,and the second predetermined angle β is set in such a manner that adifference between the first predetermined angle α and the secondpredetermined angle β can be used to determine a fact that the driverreduces the steering angle δ intentionally.

If the steering angle δ is greater than the second predetermined angle βso that the answer of step S32 is YES, the routine progresses to stepS19. By contrast, if the steering angle δ is smaller than the secondpredetermined angle β so that the answer of step S32 is NO, the routineprogresses to step S33 to turn off the determination flag F_(lk), andthe steering torque T_(δmem) of the steering torque T_(δ) at the pointwhen the steering angle δ exceeded the first predetermined angle α isset to zero at step S34. Then, the maintenance flag F_(tqkp) is turnedoff at step S35, the upper limit value T_(u) of the correction torquesT^(r) _(add) and T^(l) _(add) is set to zero at step S36, and the lengthof time Timer_(OH) to maintain the output torque of the EPS motor 44 tothe constant torque is reset at step S37. Thereafter, each of the firstcorrection torque T^(r) _(add) and the second correction torque T^(l)_(add) is individually to zero at step S38, and the routine progressesto step S30.

Temporal changes in the steering torque T_(δ), the output torque of theEPS motor 44, the correction torques T^(r) _(add) and T^(l) _(add), andthe upper limit value T_(u) of the correction torques T^(r) _(add) andT^(l) _(add) during execution of the routine shown in FIGS. 6 to 8 areindicated in FIG. 9.

At point t0, the driver starts rotating the steering wheel 28, and hencethe steering torque T_(δ) and the output torque of the EPS motor 44 areincreased from point t0. Then, when the steering wheel 28 is rotated tothe first predetermined angle α at point t1, the output torque of theEPS motor 44 is maintained to the constant torque. In this situation,the driver still increases the steering torque T_(δ) applied to thesteering wheel 28 thereby increasing the steering torque T_(δ)continuously after point t1. Consequently, the correction torques T^(r)_(add) and T^(l) _(add) are increased from point t1.

When the correction torques T^(r) _(add) and T^(l) _(add) are increasedto the upper limit value T_(u) at point t2, the correction torques T^(r)_(add) and T_(l) ^(add) are maintained to the upper limit value T_(u).Then, when the length of time Timer_(OH) to maintain the output torqueof the EPS motor 44 reaches the predetermined period of time TM_(OH) atpoint t3, the upper limit value T_(u) of the correction torques T^(r)_(add) and T^(l) _(add) is reduced from point t3. In this situation, thecorrection torques T^(r) _(add) and T_(l) ^(add) are changed inaccordance with the steering torque T_(δ). When the upper limit valueT_(u) is reduced to the correction torques T^(r) _(add) and T^(l) _(add)at point t4, the correction torques T^(r) _(add) and T^(l) _(add) aremaintained to the upper limit value T_(u) again while being reduced inaccordance with a reduction in the upper limit value T_(u). Eventually,at point 5, the upper limit value T_(u) is reduced to zero, and thecorrection torques T^(r) _(add) and T^(l) _(add) are set to zero. Thus,the torques applied to the drive wheels 11R, 11L, 57R, and 57L inaccordance with the difference Δγ between the target yaw rate γ_(tgt)calculated based on the steering angle δ and the actual yaw rateγ_(real).

By thus executing the routine shown in FIGS. 6 to 8, a yaw rate greaterthan the target yaw rate γ_(tgt) achieved in accordance with thesteering angle δ of the steering wheel 28 can be achieved when thesteering wheel 28 is turned to the maximum rotational angle. Accordingto the embodiment, therefore, a turning performance of the vehicle canbe improved.

In addition, the upper limit value T_(u) of the correction torques T^(r)_(add) and T_(l) ^(add) is reduced when the length of time Timer_(OH) tomaintain the output torque of the EPS motor 44 reaches the predeterminedperiod of time TM_(OH). According to the embodiment, therefore,excessive temperature rise in the motors rotating the outer pair ofwheels can be prevented to limit thermal damages on the motors.

Further, when the length of time Timer_(OH) exceeds the predeterminedperiod of time TM_(OH), the warning is emitted to urge the driver toreduce the steering torque T_(δ) to rotate the steering wheel 28.According to the embodiment, therefore, the output torque of the EPSmotor 44 may be reduced and hence thermal damage on the EPS motor 44 mayalso be prevented. In addition, if a yaw rate is reduced when thesteering torque T_(δ) is reduced by the driver, uncomfortable feelingresulting from the reduction in the yaw rate can be reduced by reducingthe correction torques T^(r) _(add) and T^(l) _(add).

Although the above exemplary embodiment of the present application havebeen described, it will be understood by those skilled in the art thatthe present disclosure should not be limited to the described exemplaryembodiments, and various changes and modifications can be made withinthe spirit and scope of the present application. For example, the driveforce control system according to the embodiment may also be applied toan in-wheel motor vehicle in which a motor is individually arranged ineach wheel, and to a two-wheel drive vehicle.

In addition, the steering device 27, the steering shaft 29 may also berotated hydraulically instead of the motor.

Further, the correction torques T^(r) _(add) and T_(l) ^(add) may alsobe reduced when temperatures of the EPS motor 44 and the motors 2R, 2L,2R′, and 2L′ exceed predetermined temperatures.

What is claimed is:
 1. A drive force control system, comprising: a driveunit that applies torques to a right wheel and a left wheel; a steeringdevice that turns a pair of steered wheels in accordance with anoperating amount of a steering wheel; and a controller that controls thetorques applied to the right wheel and the left wheel, wherein thecontroller is configured to: calculate a target yaw rate based on asteering angle of the steering wheel; calculate a predetermined torqueto adjust a torque of at least any one of the right wheel and the leftwheel, based on a difference between the target yaw rate and an actualyaw rate; calculate a correction torque to correct the predeterminedtorque , when the steering angle of the steering wheel is equal to orgreater than a maximum rotational angle of the steering wheel; andtransmit a signal to the drive unit to achieve a target torque of the atleast any one of the right wheel and the left wheel calculated based onthe predetermined torque and the correction torque.
 2. The drive forcecontrol system as claimed in claim 1, wherein the controller is furtherconfigured to: obtain a steering torque of the steering wheel, andcalculate the correction torque based on an increase in the steeringtorque from a point at which the steering angle is equal to or greaterthan the maximum rotational angle, when the steering torque is increasedto rotate the steering wheel to an amount equal to or greater than themaximum rotational angle.
 3. The drive force control system as claimedin claim 1, wherein the controller is further configured to reduce thecorrection torque when a length of time to rotate the steering wheelexceeds a predetermined period of time.
 4. The drive force controlsystem as claimed in claim 1, wherein the controller is furtherconfigured to transmit a warning to a driver when a length of time torotate the steering wheel exceeds a predetermined period of time.
 5. Thedrive force control system as claimed in claim 1, wherein the steeringdevice includes a motor that applies a torque to a transmissionmechanism between the steering wheel and the steered wheels, and whereinthe controller is further configured to: obtain a steering torque of thesteering wheel, and control an output torque of the motor in accordancewith the steering torque of the steering wheel, and maintain the outputtorque of the motor to the steering torque at a point when the steeringwheel is rotated to the maximum rotational angle, until the steeringangle of the steering wheel is reduced to a second predetermined anglethat is smaller than the maximum rotational angle.
 6. The drive forcecontrol system as claimed in claim 1, wherein the controller is furtherconfigured to set an upper limit value of the correction torque.
 7. Thedrive force control system as claimed in claim 1, wherein the controlleris further configured to obtain a steering torque of the steering wheel,and calculate the correction torque to correct the predetermined torquein accordance with the steering torque.
 8. A drive force control system,comprising: a pair of motors that are configured to apply torque to aright wheel and a left wheel; a steering shaft connected to a rack andpinion gear that is configured to turn a pair of steered wheels inaccordance with an operating amount of a steering wheel; a yaw ratesensor configured to detect an actual yaw rate; a controller thatcontrols the torques applied to the right wheel and the left wheel,wherein the controller is further configured to: calculate a target yawrate based on a steering angle of the steering wheel; calculate apredetermined torque to adjust a torque of at least any one of the rightwheel and the left wheel, based on a difference between the target yawrate and the actual yaw rate; calculate a correction torque to correctthe predetermined torque , when the steering angle of the steering wheelis equal to or greater than a maximum rotational angle of the steeringwheel; and transmit a signal to the pair of motors to achieve a targettorque of the at least any one of the right wheel and the left wheelcalculated based on the predetermined torque and the correction torque.9. The drive force control system as claimed in claim 8, furthercomprising a torque sensor configured to detect a steering torque of thesteering wheel, wherein the controller is further configured to obtainthe steering torque of the steering wheel, and calculate the correctiontorque to correct the predetermined torque in accordance with thesteering torque.